Machine tool transmission and control mechanism



April 23, 1940.-

' J. B. ARMITAGE MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM Filed May 15, 1937 13 Sheets-Shea}. 1

INVENTOR JOSEPH B. ARMITAGE ATTORNEY April 23, 1940. J. a. ARMITAGE MACHINE TQQL TRANSMISSION AND CONTROL MECHANISM Filed May 15, 1937 15 Sheets-Sheet 2 m L Om llll llll ll INVENTOR JOSEPH B. ARMITAGE BY W/KV J ATTORNEY "Am-i123, 1940. J. a. ARMITAGE 2,198,102

' 5' MA QHINE" 'roop TRANSMISSION AND CONTROL MECHANISM Filed May 15, 1957 -1:s Sheets-Sheet :s.

INVENTOR Y JOSEPH B.ARM|TAG ATTORNEY nv 8 a2 0 5. N: 2. m: 8. fl 0 WM. 5. Q. L 5 .1, up. n: n G n J P no. *0. h- I/ n n n I I I [/l n I. u 1 g m 8 5. 8 Q 8 2 .2 a 1% V cm. a? FF a? 5.

April 23, 1940; 4.1a;Ammic: I 2,198,102

- MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM Filed lay 15, 1931 13 Sheets-Sheet 4 INVENTOR a Mlm I i 1: H4 M211.

JoscPn Bjlnmme: 77.41% 5mm ATTORNEY April 1940. I J. a. ARMITAGE 2,198,102

MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM Filed May 15, 1937 13 Sheets-Sheet 5 INVENTOR JossPu B. ARMITAGE W49 WW ATTORNEY April 1940. J. B. ARMITAGE 2,198,102

MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM Filed May 15, 1937 13 Sheets-Sheet 6 FIG.14

INVENTOR Joszpn B. ARMITAG:

ATTORNEY April 23, 1940. WAGE 2,198,102

MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM Filed May 15, 1937 13 Sheets-Sheet 7 as i s I 124 I i l 1 J30 I451 4 14 a 1 i I INVENTOR JOSEPH BARMITAGE FIG. 16

ATTORNEY Q m Q L E 1 J. B. ARMITAGE 2,198,102 MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM Filed May 15, 1957 13 Sheets-Sheet 8 April 23, 1940.

J. B. ARMITAGE MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM 13 Sheets-Sheet 9 Filed May. 15, 1937 INVENTOR JOSEPH B. ARMITAGE BY I (V ATTORN EY April 23, 1940.

ll nmi 11- v u Ami II/Ill! m L E April 1940- J. B. ARMITAGE 2,198,102

MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM Filed May 15, 1937 13 Sheets-Sheet 11 FIG. 24-

' 3G4 325 X I 345 2G5 266 a 3% 362. m g m W fl fi w r 350 I 1 V 3.43 w :3

li 35c 1 1 FIG 25 INVENTOR Joszpn B. ARMI'TAGE ATTORN EY April 1940- J. a. ARMITAGE Q 2,193,102

MACHINE TOQL TRANSMISSION AND CONTRQL MECHANISM 13 Sheets-Sheet 12 i J INVENTOR'K JOSEPH B. A BY W Filed May 15, 1937 RMITAGI:

4v W ATTORNEY April 0- I J. B. ARMITAGE V 2,198,102

MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM Filed May 15, 1937 I3 Sheets-Sheet 13 INVENTOR JOSEPH B ARMITAGE' ATTORN EY Patented Apr. 23, 1940 UNITED STATES PATENT OFFICE CONTROL ME Joseph B. Armitage, Wauwatosa, Wia, assignor to Kearney &' Trecker Corporation. West Allis,. Wis., a corporation oi Wisconsin Application May 1937, Serial No. 142,781

46 Claims.: (Cl. 90-21) This invention relates generally to machine tools, and more particularly to improved trans- :nission and control mechanism for a machine 6 A general object of the invention is to provide an improved transmission mechanism and control apparatus for actuating and automatically controlling a movable element of a machine tool.

Another object of the invention is to provide an 7 it) improved transmission mechanism and control i6 changing and reversing mechanism for the power transmission train of a machine tool.

Anotherobject is to'provlde in a machine tool an improved rate-changing and reversing mechanism that may be operated either manually or 20. automatically.

Another object is to provide an improved ratechanging and reversing mechanism embodying mechanical clutches arranged for selective engagement to effect movement in either direction at either of two rates of speed.

Another object is to provide a-rate-changing and reversing mechanism utilizing mechanical clutches and having control means arranged to prevent engagement of the clutches in undesired combinations.

Another object is to provide control mechanism for the clutches of a rate-changing and reversing mechanism having means to engage the clutches in pre-selected combinations to effect operation 35, at a selected rate in either direction.

Another object is to provide control mechanism for the clutches of a mechanical rate-changing and reversing mechanism having a single element movable to eifect flve combinations of po- 40; sitions of the clutches including a neutral position and positions resulting in operation at either of two speeds in either direction.

Another object is to provide an improved reversing mechanism for a machine tool transmission.

Another object is to provide an improved revers'ing mechanism for a machine tool transmission utilizing auxiliary power means to eiiect au tomatic reversal.

Another object is to provide an automatic reversing mechanism for a machine tool transmission that may be adjusted readily to effect reversal of a driven machine element or to stop the movement thereof selectively at either or both 58 ends of its stroke.

Another object is to provide automatic reversing mechanism for a machine tool transmission that may be adjusted to efiect reverse movement accurately and selectively ateither of two rates or speed. 6

Another object is to provide an improved mechanical rate-changing and reversing mechanism for a milling machine table, having a power actuated reversing device that is adjustable to eifect reverse movement'either at rapid traverse rate or it at feed rate., x Another object is to provide an improved reversing control mechanism actuated by power derived from the mechanical transmission mechanism. it

Another object is to provide an improved electrically actuated automatic reversing mechanism for a machine tool transmission.

Another object is to provide an improved reversing mechanism having hydraulically actuated an automatic reversing means.

A further object is to provide an improved hydraulic control system for a machine tool.

According to this invention, an improved transmission mechanism for driving a movable element 25 of a machine toolfor example, the work table of a milling machine, is arranged to be adjusted manually or automatically to efiect movement of the table in either direction and at either of two rates. Adjustment of the mechanism is eflected 30 by engaging or disengaging mechanical clutches, an over-running clutch being provided for driving the mechanism at the lower rate of speed in order that transition from one rate of speed to the other may be efiected without stopping move- 5 ment of the table. The mechanical clutches are controlled by a cam shifting mechanism arranged to effect a predetermined sequence of clutch engagements and to prevent engagement of the clutches in inoperative combinations, a single 40 control lever being provided for moving the cam to efiect manual shifting of the clutches. Automatic change in rate is effected in response to movement of the table by positively operating trip dogs acting directly upon the cam shifting mech- 45 anism. To effect reversal of the direction of movement automatically in response to table movement, supplemental dogoperated power ,reversing mechanism is provided for moving the clutches through neutral position. The supple- 50 mental power reversing mechanism may be actuated mechanically from the table transmission mechanism, or it may be actuated electrically or by means of hydraulically operated power elements. Control means are provided for adiusting the mechanism to effect reversal at either of the two rates of speed or to render the reversing mechanism non-responsive to movement of the table in either or both directions of travel.

The invention is exemplified herein by three embodiments thereof, illustrating the'mechanical, the electrical, and the hydraulic power reversing mechanism respectively; however, it is to be understood that these particular embodiments are illustrative only, and that various other structural forms within the range of equivalents of the features defined in the claims may be employed in practicing the invention.

The foregoing and other objects of the invention, which will become more fully apparent from the following detailed descriptions of mechanisms exemplifying the three preferred embodiments thereof, may be achieved by the apparatus described herein in connnection with the accompanying drawings, in which:

Figure 1 is a view in left side elevation of a milling machine exemplifying a machine tool of the type in which the present invention may be incorporated, parts of the machine frame having been broken away to show the internal driving mechanism.

Fig. 2 is a view in vertical section of parts of the machine taken longitudinally of the work table, substantially on the plane represented by the line 2-2 in Fig. 1, and showing the table-driving. rate-selecting and reversing mechanism.

Fig. 3 is a fragmentary view partly in transverse section taken on the plane represented by.

the line 3-3 in Fig. 2. showing the table driving screw and nut mechanism and the table screw guard.

Fig. 4 is a fragmentary view in front elevation of the clutch shifting mechanism for the rate selecting and reversing apparatus.

Fig. 5 is a fragmentary view in front elevation generally similar to Fig. 2 but with the clutch shifting apparatus of Fig. 4 superimposed thereon, and with control mechanism for the clutches shown partly in diagram in its operating relationship therewith.

Figs. 6, 7, and 8 are fragmentary views showing the rate selecting and reversing clutches of Figs. 2 and 5 in their different operating relationship for effecting the various modes of operation of the mechanism.

Figs. 9, l0, and 11 are views in front elevation of the lower part of the machine, showing the respective control panels and operating levers for the mechanical, the electrical, and the hydraulic power reversing apparatus constituting the three embodiments of the invention herein disclosed.

' Fig. 12 is a frontal view, partly in section substantially on the plane represented by the line l2-l2 in Fig. 14, showing the control apparatus for effecting automatic reversal by mechanically actuated supplemental power means.

taken on the plane represented by the line IO-IU in Fig. 12.

Figs. 17, 18, and 19 are. frontal views similar to Fig. 12 but showing the mechanical reversing mechanism in various positions assumed during a power reversing operation.

Fig. 20 is a diagrammatic frontal view generally similar to Fig. 12 but showing apparatus for effecting automatic reversal by electrical means.

Fig. 21 is a view in vertical transverse section generally similar to Fig. 14 but showing the electrical reversing mechanism, taken substantially on the plane represented by the lines 2l-2l in Figs. 10 and 20.

Fig. 22 is a schematic wiring diagram of the electrical control circuit for the electrically operated automatic reverser.

Fig. 23 is a view in horizontal section in part of the hydraulic reversing mechanism taken on the plane represented by the line 23-23 in Fig. 24.

Fig. 24 is a partially diagrammatic frontal view taken largely in vertical section on the plane represented by the line 24-24 in Fig. 26 and generally similar to Figs. 12 and 20 but showing the apparatus for effecting automatic reversal by hydraulically operated means.

Fig. 25 is a view in horizontal section showing somewhat diagrammatically parts of the control mechanism for the hydraulic reverser. taken substantially on the plane represented by the line 25-25 in Fig. 24.

Fig. 26 is a view in vertical transverse section generally similar to Figs. 14 and 21 but showing the hydraulic reversing mechanism taken substantially on the plane represented by the line 26-28 in Figs. 11 and 24.

Fig. 27 is a fragmentary view in vertical section of part of the hydraulic control mechanism taken on the plane represented by the line 21-21 in Fig. 24; and

Fig. 28 is a schematic diagram of the hydraulic control circuit for the hydraulically operated automatic reverser.

The particular machine tool illustrated in the drawings as exemplifying apparatus of the class in which the present invention may be embodied, is a milling machine of the bed type shown as viewed from the left side, some of the details of mechanism not directly concerned with the present invention having been omitted for the sake of more clearly showing the major elements.

Referring more particularly to the drawings, and especially to Fig. 1 thereof, the milling machine there generally depicted comprises essentially a hollow frame or bed 30, constituting the main body or base of the machine and forming a housing for the transmission and controlling mechanism embodying the invention. On its upper surface adjacent to its forward edge. the

-bed 30 carries a work supporting table 3| that is slidably mounted in ways 22 for longitudinal reciprocatory movement relative to the bed.

Mounted on the bed 30 back of the table 3| is an upstanding column 33 that carries a rotatable tool supporting spindle 34 for mounting a rotary cutting tool in cooperating relationship with a workpiece carried by the work-supporting table 3!.

To provide for movement of the spindle 24 in a plane transverse to the table 3|, the spindle is journaled in a quill 35 that is slidably mounted for horizontal axial movement in a spindle-carrying head 36, a rack and pinion mechanism 31 being provided for effecting movement of the quill. A pair of overarms 33 areslidably mounted in the spindle carrying head 36 above the quill 35 for supporting a cutter arbor in well-known manner, the arms being also arranged to support the quill by means of a yoke 39 when it is extended forwardly from the column 33.

To provide for vertical movement of the spindle 34 relative to the table 3|, the entire spindlecarrying head 36 is slidably mounted in the column 33 in such manner that it may be adjusted vertically to any predetermined position and clamped there by well-known means not shown. By these adjustments relative movement between a cutter and a workpiece may be effected in three mutually normal planes.

For rotating a cutting tool in operating upon a workpiece, the spindle 34 is provided at its inner end with a driving gear wheel 42 which meshes with a pinion 43 carried by a housing 44 that is attached to the quill 35, the gear and pinion constituting a reduction drive mechanism for the spindle. Power is transmitted to the pinion 43 by means of a horizontally disposed splined shaft 46, which isjournaled in the head 36 and has sliding connection with the pinion to accommodate the longitudinal movement of the quill 35 relative to the head. The splined shaft 46 is provided within the head 36 with a bevel gear 41 which meshes with a bevel gear 48 on-the upper end of a vertically disposed shaft 49, also journaled in and carried bythe head 36. The vertical shaft 49 has splined connection at its lower end with a bevel gear 5| that is journaled in the bed 36, the arrangement being such that the sliding head 36 and the shaft 49 may move vertically while maintaining driving connection with the gear 5|.

The bevel gear 5| in the bed 36 meshes with a cooperating bevel gear 52 mounted on the inner end of a horizontal shaft 53 which extends, outward into an accessible speed changer compartment 54 at the left side of the machine. Detachably mounted on the outer end of the shaft 53 is a pick-off gear 55 which meshes with a complementary pick-off gear 56 mounted on the outer end of a shaft 51 disposed below and parallel with the shaft 53, the arrangement being such that by interchanging the pick-off gears 55 and 56v or by substituting another pair of gears of different ratio, the speed at which the spindle 34 is to be driven may be adjusted. The shaft 51 is provided at its inner end with a bevel gear 58 that meshes with a cooperating bevel gear 59 on a main driving shaft 66 extending from the front to the back of the machine transversely of the shafts 53 and 51.

The main driving shaft 66 may be connected by means of a friction clutch 6| directly with the front of the machine.

the shaft of a driving motor 62, which is shown connected by a flange mounting to the back of the bed 36. For stopping the shaft 66 when the clutch 6| is disengaged to disconnect it from the motor 62, there is provided a brake 63 which is arranged to be operated by actuating mechanism 64 that is primarily provided for actuating the clutch 6|, and that includes a starting lever 65 at the front of the machine arranged to be moved in one direction to engage the clutch and in the other direction to engage the brake.

To provide for moving the work table 3| at feed rate, power is transmitted from the motor 62 through the clutch 6| to the main driving shaft 66 which is extended forward into anaccessible feed rate-changing compartment 61 at Removably mounted a pick-oil gear 69 which meshes with a'complementary pick-off gear 69 on the forward-end of may be interchanged or another pair of similar pick-off gears having another ratio may be substltuted therefor in well-known manner to adjust the rate of feeding movement of thetable. From the feed rate changing pick-off gears, power is transmitted at the selected feed rate through the shaft 16 whichis connected by a safety release clutch 1| with a co-axially disposed shaft 12 carrying a worm 13 that meshes with a worm wheel 14 constituting-the feed'rate driving element of the table driving rate changing transmission and reversing mechanism to which the present invention is particularly directed. Since the main driving shaft 66 is driven only when" the main clutch 6| is engaged, the table 3| may be driven at feed rate only while the spindle 34 is operating.

In order that the table 3| may be driven at rapid traverse rate regardless of whether or not the spindle 34 is operating, an independent driving connection is provided directly from the shaft of the motor 62 by means of a train including a gear 16 mounted directly on the motor shaft and meshing with an idler gear 11 which in turn drives a gear 18 on a rapid traverse shaft 19 disposed generally parallel with the main driving shaft 66. The shaft 19 is connected by means of a safety release clutch 86 with a co-axially disposed shaft 8! which extends forward and is provided at its forward end with a bevel pinion 82 meshing with a bevel pinion 83 that is disposed co-axially with the feed rate driving worm wheel 14, and that constitutes the continuously operating rapid traverse rate driving element of the rate changing and reversing mechanism.

Referring to Fig. 2 of the drawings, the worksupporting table 3| is propelled longitudinally relative to the bed 36 by means of a feed screw 96 which is journaled at its ends in the ends of the bed 36, and which cooperates with a travelling nut 9| that is attached to the table. One end of the feed screw 96 is provided with a squared portion 92 for receiving a crank or the like, not shown, for turning the screw manually to position the table for setting up work or for hand feeding.

To protect the feed screw 96. from foreign substances, such as chips or cooling fluid, which might drop onto it, particularly when the table is moved to an extreme position exposing part of the feed screw, there is provided a guard 93,

preferably of semi-circular shape as shown in Fig. 3, and that is disposed above and concentric with the screw 96. The guard 93 is secured at each end to the end of the bed 36 by attaching screws, as may be seen in Figs. 14, 21, and 26, in manner to protect the feed screw 96 throughout its entire length. As shown in Fig. 3, the travelling nut 9| completely encircles the feed screw 96 and is provided with lugs or ears 94 extending from each side thereof below its centerline and which are attached to the bottom of the table by means of screws 95, the nut being shaped to provide between its upper portion and the lower part of the table a segmental or semicircular groove or channel 96 within which the guard member 93 may have relative longitudinal movement. By this arrangement, the driving screw 96 may be placed relatively high 'Within the longitudinal groove in the bottom of the .on the forward end of the extended shaft 66 is 'a shaft. 16 disposed parallel to and above the main shaft 66. The pick-oil gears 68v and 69 table forming the arcuate passageway 98, and

the table screw may be completely protected from damage by foreign substances falling upon it.

For rotating the table screw 80 by power, a

driving gear wheel IN is keyed to the screw near the left end of the bed, as shown in Fig. 2. The screw driving gear I-I meshes with and is driven by a clutch gear I02, which is rotatably mounted on a stub shaft I03 fixed in the frame 80 parallel to and below the feed screw 90 and con- .stituting part of the rate changing and reversing mechanism, the arrangement being such that the clutch gear I02 may be engaged by power driving means to drive the feed screw 80 in the one direction. For driving the feed screw 90 in the other direction, there is provided a clutch gear I04 which is rotatably mounted on a shaft I journaled in the bed 30 parallel to and below the fixed shaft I03, the clutch gear I04 being meshed with an idler gear I08, which in turn meshes with the clutch gear I02 as shown in Figs. 14 and 26. The table driving clutch gears I02 and I04 are mounted in fixed positions on the shafts I03 and I05 and each gear is provided on one face with clutch teeth or jaws I01 presented for engagement by cooperating teeth on a driving clutch member.

Power for moving the table 3| at feed rate is transmitted from the motor 62, as previously explained, through the main clutch 6|, the main driving shaft 60, and the feed rate changer, to the worm l3 driving the cooperating worm wheel I4. As shown in Fig, 2, the worm wheel 14 is keyed to a shaft I08 that is journaled in the frame 30 co-axially with the shaft I00 and that is operatively connected thereto by means of an over-running clutch mechanism I 09 in such manner that the shaft I05 may be driven at feed rate from the shaft I08 but is free to rotate at a faster rate by reason of the over-running clutch connection.

Slidably keyed on the shaft I05 for axial movement is a shiftable clutch gear III which meshes continuously with a similar clutch gear II2 slidably mounted on the stationary shaft I00, the two gears being arranged to rotate in opposite directions and at equal speeds. As shown, each of the slidably mounted clutch gears is provided on each face with clutch teeth or jaws II3, the gears being shown in neutral or central position in Fig. 2 with the clutch teeth H8 presented for selective engagement with cooperating clutch teeth at either side thereof.

To effect movement of the table 3| at feed rate to the right, for example, the slidably keyed clutch gear III on the shaft I05 is moved to the right to engage its teeth I I3 with the teeth I01 of the table driving clutch gear I04, as shown in Fig. 6. For driving the table at feed rate to the left, the teeth of the clutch gear III are disengaged from the teeth of the clutch gear I04, and the oppositely rotating sliding clutch gear II2 on the shaft I03 is moved to the right to engage its teeth with the teeth of the table driving clutch gear I02, as shown in Fig. '7, thereby driving the feed screw in the reverse direction.

Power for moving the table 3| at rapid traverse rate is transmitted from the motor 62, as previously explained, independently of the main clutch 6| by the directly driven rapid traverse gear train and the shafts I9 and Ill, to the bevel gear 02 that meshes with the bevel gear 83, which is rotatably mounted concentric with the worm wheel I4 and the shaft I05.

As shown in Fig. 2, the bevel gear 83 is keyed to an extending hub or sleeve of a rapid traverse clutch gear II4 that is rotatably mounted on the shaft I05 in position to cooperate with the sliding clutch gear III. The clutch gear II4 meshes with and drives an oppositely rotating rapid traverse clutch gear H5 that is in turn rotatably mounted on the stationary shaft I03 in cooperating relationship with the sliding clutch gear H2. The rapid traverse clutch gears H4 and H5 are mounted in fixed positions on the shafts I03 and I05 and present clutch teeth H6 for engagement by the clutch teeth H3 of the slidably mounted clutch gears III and. H2. The gears H4 and H5 rotate at equal speeds and in opposite directions at rapid traverse rate whenever the driving motor 62 is running.

When the table is being driven at feed rate to the left-for example, with the clutches in the position shown in Fig. 7 as previously explainedand it is desired to drive the table in the same direction at rapid traverse rate, it is merely necessary to move the slidable clutch gear III to the left to engage its clutch teeth II3 with the clutch teeth II6 of the rapid traverse clutch gear 4- as shown in Fig. 8, whereupon the engaged clutch gears and the table driving mechanism will rotate at rapid traverse rate, the shaft I05 being free to turn at the faster rate by reason of the overrunning clutch I09.

Because of the over-running clutch driving connection in the feed rate drive to the table 3|, the transition in driving rate from feed to rapid traverse or from rapid traverse to feed may be effected without stopping movement of the table 3|. Thus to change from rapid traverse drive to the left back to feed to the left, it is merely necessary to disengage the sliding clutch I I I from the rapid traverse clutch I I4, whereupon the feed rate driving connection is immediately re-established by the over-running clutch I09.

To operate the table 3l at rapid traverse rate to the right, the sliding clutch gear III is moved to-engage the table driving clutchgear I04 in mannerto drive the table to the right at feed rate, and then the sliding clutch gear H2 is moved to the left to engage the rapid traverse clutch gear H5 to change the rate to rapid traverse, the clutches then being in the position shown in Fig. 5. Although positive clutches of the jaw type are shown in the drawings, it is to be understood that any other suitable clutches such as friction clutches may be utilized in their stead.

The mechanism for shifting the slidable clutch gears III and H2 is shown in Fig. 4 and comprises shifting forks H8 and I I9, which engage the respective clutch gears and are carried on shifting rods I and I2I respectively, that are slidably mounted in the bed 30. The rods I20 and I2l are provided with shifting arms I22 and I23 respectively, which carry at their lower ends cam followers I24 and I25 respectively for engaging a cam-shifting mechanism by means of which movement of the clutches is controlled. To avoid jamming of the shifting mechanism, the shifting forks H8 and H9 are connected to the shifting rods I20 and HI by springs I26 in such manner that should the cooperating teeth of a pair of the clutches fail to intermesh when the shifting mechanism is actuated, the springs I26 will permit the associated shifting rod to move relative to the shifting fork, and will exert a continuous resilient pressure to effect engagement as soon as the gearing is turned to bring the teeth into meshing relationship.

In Fig. 5, the clutch shifting mechanism of Fig.

4 is shown disposed inoperating position relative to the shiftable clutch mechanism, and the cam mechanism for effecting the shifting in predetermined sequence is'indicated diagrammatically. As shown, the shifting mechanism includes a cam plate I30 having cam grooves I3I and I32 which engage respectively with the cam followers I24 and I25 of the shifting arms I22 and I23, the arrangement being such that when the cam plate I is turned about its axis, the cam grooves I3I and I32 will cause the clutches to be shifted in predetermined sequence and will prevent engagement of the clutches in any combination which would look the mechanism or might result in damage thereto. I

For shifting the clutches manually, there is provided a shifting lever I35 mounted on the front of the machine and directly connected to the cam plate I 30 for turning it about its axis. As indicated in Fig. 5, the lever I35 may be moved to any one of five positions, a detent mechanism including a spring-pressed plunger I 36 disposed to engage any one of five notches I31 in the plate I30, being provided to retain the lever in any selected one of its positions.

With the lever in the position A shown in full lines in Fig. 5, the shiftable clutches I II and H2 are positioned in engagement with the clutches I04 and H5 respectively to effect movement of the table 3| to the right at rapid traverse rate as previously described. When the lever is moved to position B, the clutch H2 is moved out of engagement with the rapid traverse clutch I I5 to the neutral position as shown in Fig. 6, and the table will then be driven at feed rate to the right by means of the clutch II I. Upon shifting the lever to the neutral position C, the clutch I I I is moyed out of engagement with the table driving clutch I04, thus placing both shiftable clutches in the neutral position as shown in Fig. 2, thereby stopping the table. Upon moving the lever to position D, the clutch I I2 is moved into engagement with the table driving clutch gear I02, as shown in Fig. 7, to drive the table to the left at feed rate. Shifting the lever to position E moves the clutch gear II I into engagement with the rapid traverse clutch II4, as shown in Fig. 8, to drive the table at rapid traverse rate to the left. It will be noted that in moving the lever I35 from any one of its positions to an adjacent position, only one of the movable clutch elements is engaged with or disengaged from a cooperating clutch element.

For automatically effecting change in the rate of movement of the table, or forstopping the 55' table automatically at a predetermined position,

suitable trip dogs may be mounted at predetermined positionsin a T slot I40 in the forward edge of the table 3I for cooperating with a pair of tripping posts I and I 42 mounted for vertical endwise movement in the bed 30 as shown in Fig. 5. The trip posts I and I42 are operatively connected at their lower ends to the cam plate I30 at opposite sides of its center in such manner that the cam plate may be turned by vertical movement of either one of the posts. Two trip posts are provided in order that one of the posts may be acted upon by cooperating trip dogs when the table is moving in one direction and the other post may be effective -when the table is moving in the other direction. To this end the trip post I is provided at its top with a forwardly projecting lifting lug I43 and the post I42 is provided with a similar but rearwardly projecting lifting lug I44, the arrangement being such that the cooperating trip dogs on the table operate in different planes for effecting control in each directiozi. As shown in Fig. 5, with the control lever I35 positioned to move the table 3| to the right the trip post I is elevated into position to present the lug I43 for engagement by its cooperating trip dogs in the forward plane while the trip post I42 is depressed below the line of action of its cooperating do'gs.

When the machine is operating automatically, I

the trip dogs in the forward plane, for instance, may act upon the-trip post I while the table is moving to the right to change the rate of travel from rapid traverse to feed or vice versa, or to stop the table by movingthe post down to neutral position. However, after the table has been stopped by moving the trip post and the shiftable clutches to neutral position, it is apparent that further movement of the clutch shifting mechanism must be accomplished by means not dependent upon movement of the table. Consequently in order to effect reversal of the direction of movement of the table 3| automatically, auxiliary power reversing means must be provided to move the cam shifting mechanism through the neutral .reversal of the table when operating in either direction. The auxiliary power reversing mechanism may be actuated by mechanical means, by electrical means, or by hydraulic means. Fig. 9 shows the front of the machine provided with a control panel associated with mechanically actuated reversing means; Fig. 10 shows a control panel associated with electrically actuated reversing means; and Fig. 11 illustrates a control panel associated with hydraulically actuated reversing mechanism.

Referring now to Fig. 12 of the drawings, the power reversing mechanism there illustrated exemplifies a reverser actuated by auxiliary power derived from the mechanical drive train, and comprises essentially a spring urged reversing plunger or ram I50 slidably mounted for vertical movement in the frame of the machine in manner to be forced downward by a spring I5I to move the clutch shifting mechanism through the neutral position in response to movement of one of two reversing trip rods I 45a or I4Iia by the cooperating reversing dog I4'I or I48. The reversing plunger I is normally retained in its upper position with the spring I5I compressed, by means of a latch I52 that engages a shoulder I53 on the plunger I50, as best shown in Fig. 14.

The latch I52 is fixed on a horizontal shaft I54, as shown in Fig. 15, that carries tripping arms I55 and I56 respectively, slidably keyed thereon in position to engage slots in the reverse tripping rods H511. and I46a respectively. When one of the trip rods is depressed to initiate a reversing action-for example, the reversing trip rod 50,- the cooperating tripping arm I55 is moved down to turn the shaft I54 clockwise as seen in Fig. 14, thereby withdrawing the latch I52 from engagement with the shoulder I53 and permitting the spring I5I to force the plunger I50 downward in the manner shown in Fig. 19. As shown in Figs. 12, 17, 18, and 19, the lower end of the plunger I50 is pointed to present sloping faces, one of which engages one side of a detent I56 which is associated with a clutch shifting cam plate Ia corresponding to the cam plate I30 of Fig. 5, in manner to turn the detent and the cam plate to the position shown in Fig. 19 to effect shifting of the clutches for reversing the direction of movement of the table.

At the termination of the downward movement of the plunger I50, the shoulder I53 thereof engages an abutment I60 of a power engaging control rod I6I which constitutes a stop for the plunger to limit its movement to a predetermined position and also constitutes part of a shifting device for engaging a power operated mechanism for returning the plunger to its initial raised position. As shown in Figs. 12 and 15, the control rod I6I is provided near its upper end with a slot I62 which engages one end of a bell crank I63 in manner. to turn the bell crank clockwise, as shown in Fig. 19, when the shoulder I53 of the plunger I50 engages the abutment I 60. The other arm of the bell crank I63 engages a clutch spool I64 and forces its teeth into engagement with complementary teeth on a clutch gear I65. As shown in Fig. 2, the clutch gear I65 meshes with a gear I66 on the end of a jack shaft 161, which carries another gear I66 that meshes with the constantly rotating rapid traverse cl h gear I I4, whereby the shaft I61 and associate gearing are constantly driven at uniform speed.

When the clutch I64 is engaged with the clutch gear I66, a shaft I10 on which the clutch I64 is slidably keyed is coupled to the clutch gear I65 and is caused to rotate therewith. As shown in Figs. 14 and 15, the shaft I10 is provided with a segmental pinion "I that engages rack teeth I12 on the back side of the plunger I50, and rotation of the shaft I10 through engagement of the clutch I64 causes the pinion "I to turn in direction to lift the plunger I50 upward to its latched position. When the shoulder I53 of the plunger I50 is moved up past the latch I52, it engages an abutment I13 on the control rod I6I and moves the rod upward in manner to turn the bell crank I63 counter-clockwise and to disengage the clutch I64, whereupon rotation of the shaft I10 ceases, the plunger I 50 being retained in its raised position by the latch I52 ready for a subsequent reversing action.

To insure that the pointed plunger I50 will engage the proper face of the detent I56 to effect reversal, the detent is arranged to be moved relative to the cam plate I30a through a limited angle, and means are provided for causing the actuating reversing trip rod to swing the detent I54 to the proper side of the plunger I50 prior to tripping the plunger. As shown in Fig. 12, a lower extension of the detent I56 is provided with an arcuate slot I15 which receives a pin I16 secured to the cam plate I30a constituting a lostmotion connection between the detent and the cam plate. A rack bar I16 is provided for moving the detent I58 relative to the cam plate, the bar being slidably mounted in a horizontal position and having rack teeth I16 disposed to engage gear teeth I60 on the hub of the detent I56. The ends of the rack bar I16 are chamfered to present slanting surfaces I6I disposed to cooperate with complementary slanting surfaces I62 on the lower ends of the reversing trip rods Ia and I46a.

As best shownin Fig. 18, when one of the reversing trip rodsfor instance, the trip rod I45a,is moved downward by a reversing dog,

the slanting surface I62 at its lower end engages the slanting surface I6I of the rack bar I16, forcing it inwardly to the right to cause the detent I56 to turn to the left relative to the cam plate I30a to the position shown in Fig. 18 for receiving the descending reversing plunger I in manner to eflect reversal to the left. The rack bar I16 is provided in its lower surface near its ends with detent notches I63 which are engaged by spring-pressed ball detents I64 that tend to move the rack barto central position. Each of the reversing trip rods I45a and I460. is provided with a spring I65a as shown on rod I46a in Fig. 12, to return it to raised position after being depressed by a reversing dog.

The abutment I on the control rod I6I is positioned to engage the shoulder I53 of the reversing plunger I60 when the cam plate I300. has been turned by the detent I56 to a position resulting in reversal of the table at rapid traverse rate, as shown in Fig. 12. If it is desired to effect reversal of the table at feed rate, the control rod I6I may be turned about its axis to present an abutment I61 for engagement by the shoulder I53, as shown in Figs. 17, 16, and 19, to stop the downward movement of the plunger I50 at a point at which the cam plate I300 has been turned only sufliciently to shift the clutches to effect reversal at feed rate. For turning the control rod I6I to control the rate at which reversal occurs, there is provided a slidably mounted control bar I66, best shown in Fig. 13, having rack teeth I60 meshing with elongated gear teeth I6I on the lower end of the rod I6I. The bar I66 extends horizontally through the forward wall or control panel of the machine and is provided at its outer end with an operating knob I62, as shown in Figs. 9, 13, and 14. A detent mechanism I63, Fig. 14, is provided to position the rate selecting bar I66 in either its inner or its outer position for eflecting reversal either at rapid traverse rate or at feed rate respectively.

Referring particularly to Fig. 5, the table 3I is there shown provided with trip dogs arranged to effect an automatic or continuous cycle of operation including intermittent or skip milling and automatic reversal at rapid traverse rate. Upon the operator's moving the lever I 35 to the position A as shown in full lines, the work table 3| is driven to the right at rapid traverse rate to move a workpiece into position for engagement by a cutter in the spindle 34. When the workpiece arrives at the cutter, a feed dog I secured in the T slot I40 engages the tripping post I and moves it down, turning the cam plate I30 and the lever I35 to position 3" to change the rate of movement from rapid traverse to feed.

After the first workpiece has been fed past the cutter, a rapid traverse lifting dog I66 engages the lower side of the forwardly projecting lug I43 of the trip post I, and raises the trip post back to rapid traverse position for quickly advancing the table to bring a second workpiece into position beneath the cutter. A second feed dog I61 then forces the trip post I down to feed position and feeding movement of the table continues until the second workpiece has been fed past the cutter. Y

Referring now to Figs. 17, 18, and 19, showing the mechanical reversing mechanism, Fig. 17 shows the feed dog I61 passing over the trip post In during the final out. At the end of the table stroke to the right, a stop dog I88 engages the trip post I 4 la, forcing it downward positively, as shown in Fig. 18, to partially disengagethe feed driving clutch regardless of the driving load on the clutch teeth. At the same time, the reversing dog I41 engages the reversing trip rod 5a,

- forcing it down to turn the reversing detent I58 to the left for positioning it for engagement by the plunger I58, as previously explained. After the stop dog I88 has moved the trip plunger I4Ia far enough to partially disengage the teeth of the clutch operating under the feeding load, but not far enough to completely disengage the driving clutch, the reversing -dog I41 causes the trip rod I45a to unlatch the reversing plunger I58 which then descends upon the detent I58, as shown in Fig. 19. Since the clutch teeth have by this time been forced nearly to disengaged position, only moderate force is needed to complete the disengaging movement of the driving clutch and to move the cam actuating mechanism through the neutral position to promptly engage the clutch required for driving the table in the reverse direction at feed rate, the rate selecting control rod I6I being shown in Fig. 19 in position to effect reversal at feed rate.

As the trip dogs are arranged in Fig. 5, it is preferable to effect reversal at rapid traverse rate and movement of the table to the left continues at rapid traverse rate until a feed dog I 89 engages the trip post I42 to move it down to feed position. The table may then be moved alternately at feed rate and rapid traverse rate through a cycle similar to that efiected by the trip dogs I85, I98, and I91 until the end of the stroke in the other direction is reached, at which time a stop dog 288 engages the tripping post I42 and the reverse dog I48 engages the reversing rod I48 to again reverse the direction of movement of the table causing it to move to the right at rapid traverse rate as before explained. It is to be noted that the cam actuated clutch shifting mechanism invariably shifts the clutches through neutral position into feed position before shifting into rapid traverse position, thereby avoiding shock to the drive mechanism.

If desired, the automatic reversing mechanism may be disengaged and the table caused to stop at either end of its stroke selectively. As shown in Fig. 15, the tripping arms I55 and I58 are slidably keyed on the shaft I54 in such manner that they may be moved out of engagement with the cooperating notches in the reversing trip rods H50. and M60 respectively to render either or both of the reversing trip rods inefiective. For controlling the positions of the tripping arms I55 and I58,there are provided control levers 282 and 283 respectively which are journaled in the front of the machine, as shown in Figs. 9, 14, and 15, and are provided at their inner ends with eccentrically disposed actuating pins 284 and 285 engaging cooperating slots in the tripping arms I55 and I58 respectively, the arrangement being such that the arms may be moved from engaged posi-' tion shown in Figs. 12, 18, and 19, to disengaged position shown in Fig. 17 or vice versa, by turning the respective control cranks through one-half revolution. Each of the control cranks is provided with a spring-pressed positioning plunger 288 disposed to engage either one of two positioning holes 281 or 288 to lock the shifting arms in either the engaged or disengaged position. In the arrangement shown, when the positioning plungers 288 are engaged with the inner positioning holes 288, the tripping arms I55 and I55 engage the tripping rods la and I48a respectively to provide for reversal at both ends of the table stroke. When one crank, for instance the crank 283, is turned, as shown in Fig. 15, to engage its plunger 288 with the outer positioning hole 281, the corresponding tripping arm I88 is disengaged from the tripping rod 148a and consequently the table will not reverse when the rod I48a is depressed by the reversing dog I48. However, inasmuch as a stop dog such as the dog 288 is always used in conjunction with a reversing dog, as shown in Fig. .5, the stop dog will depress the direct acting tripping post I42 and disengage the clutch to stop the table.

According to another embodiment, constituting a modification of the invention, the automatic reversing movement is accomplished electrically by means of a reversible electric motor apparatus arranged to provide the auxiliary power necessary to move the clutch shifting mechanism through the neutral position. The particular electric reversing motor illustrated in Figs. 20, 21, and 22 of the drawings comprises essentially two solenoids 2H and 2I2 respectively, that are. arranged to rotate a clutch shifting cam plate I88b in one direciion or in the other direction under the control of switches actuated by the reversing dogs on the table. As shown, the solenoids are provided respectively with armatures 2I8 and 2I4 which are connected respectively to the ends of a bar 2 I 5 of non-magnetic material that it attached to a rack element 2I8 having rack teeth engaging gear teeth on the lower edge or the cam plate I88b, corresponding to the cam plate I38 shown diagrammatically in Fig. 5.

For controlling the solenoids 2H and 2I2, there are provided a pair of reversing trip rods H817 and H81) which are associated with control switches 2I1 and 2I8 respectively, the switches being of the quick acting or toggle type. asillustrated by the switch 2I8 in Fig. 20, to provide for closing the circuit to the cooperating solenoid without delay when the table arrives at the predetermined position at which reversal is to take p ace.

Referring to the schematic wiring diagram, Fig. 22, power for actuating the electrical reversing motor is derived from a power line conductor 228 .which may represent one side of the power line that supplies energy to the driving motor 62, or any other suitable source of energy; and flowsthrougha conductor 22 I, a disconnecting switch 222, and a conductor 223, to the reversing switch 2I1. When the reversing trip rod N51) is depressed by the reversing dog I41, the switch 2I1 is closed and the current flows through a conductor 224, a switch 225, and a conductor 228, to the winding of the solenoid 2I2, and thence through a conductor 221 to a line conductor 228, constituting the other side of the main power line. With the winding of the solenoid 2I2 thus energized, the armature 2I4 is drawn into the solenoid, moving to the right as shown in Figs. 20 and 22 to turn the cam plate I38b in manner to shift the clutches for reversing the direction of movement of the table 8| from movement to the right to movement to the left.

Upon the moving of the armature 2I4 to the right in its stroke within the solenoid 2I2, it engages a plunger 229 which opens the switch 225, thereby breaking the circuit and de-energizing the solenoid. As may be seen in Fig. 20, the switch 225 is also of the quick break or toggle type, similar to the switch 2I8. This de-energizing switch 225 is provided to prevent con- 

